JP2009121693A - Thermal stratification type heat storage tank and terminal structure of water supplying/draining flow channel of the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a terminal structure of a water supplying/draining flow channel of a thermal stratification type heat storage tank capable of realizing the flow of sufficiently-low flow velocity and high uniformity in flow velocity distribution. <P>SOLUTION: This terminal structure of the water supplying/draining flow channel formed on a branch pipe extending from a main pipe, is composed of a tip portion 10a of at least one branch pipe 10 and a head member 14 connected with the tip portion of the branch pipe, and the head member 14 is composed of a hollow body connected with the tip portion 10a of the branch pipe 10 at one of its upper and lower portions, and provided with an opening portion 28 at the other portion, and includes a water channel 20 from the tip portion 10a to the opening portion 28. The water channel 20 is composed of a single flow channel excluding the neighborhood of the tip portion 10a of the branch pipe, and formed while an area of the flow channel is minimum at a connecting portion with the tip of the branch pipe and maximum at the opening portion 28, and a speed reducing means 34 by combination of pressure loss by enlargement e1 of the flow channel area and frictional resistance in accompany with bending c1 of the flow channel, is disposed in the water channel 20. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a temperature stratified heat storage tank and a terminal structure of a water supply or drainage channel of the tank.

  It is an effective means for power load leveling to store cold water or hot water in a water heat storage tank and perform cooling or heating without moving a heat source device such as a refrigerator at the time of power peak.

  The water heat storage tank includes a mixed water heat storage tank (Patent Document 1) and a temperature stratified heat storage tank (Patent Document 2). The mixed water heat storage tank, for example, pours water from above the heat storage tank and sucks water from the bottom of the heat storage tank, so the water in the tank is agitated and the mixing loss is large. On the other hand, the thermal stratification type heat storage tank utilizes the difference in density due to the difference in the temperature of water in the tank, so that the water having a high temperature and a low density is transferred to the upper part of the tank and the density is low. This is a method in which large water is provided in the lower part of the tank. This method is effective from the viewpoint of the utilization efficiency of the water heat storage tank with less mixing loss than the mixed water heat storage tank. In addition, the temperature stratification type heat storage tank is easier to maintain the temperature stratification because the water with different depths is less likely to mix with water at different temperatures. Such a construction cost is expensive, and even when building on the ground, the cost of building construction is high.

    Therefore, it is more economical if water storage tanks with as low a depth as possible are connected and multiple tanks can be connected to ensure effective water storage, and even when water storage tanks are used using underground pits in existing buildings. Since it can be applied, there is an advantage that the application range is expanded.

    Patent Document 2 teaches two conditions to be satisfied to meet such a demand, and means for that purpose.

    The first is to reduce the water inflow / outflow rates at the water supply and drain outlets installed at various locations in each heat storage tank to such an extent that the temperature stratification is not agitated. Needless to say, if the flow rate of water is large, the temperature stratification may be disturbed far from the water supply port. As means for realizing this, it has been proposed to form the water supply port (or drainage port) with a plurality of water through holes drilled in the circumferential direction of a low-profile cylindrical distributor closed at both upper and lower ends. .

Secondly, the variation in the flow velocity between the water supply ports provided along the water supply main pipe and the variation in the flow velocity between the respective water discharge ports provided along the drainage main pipe are reduced. For example, in a water supply main pipe, the flow velocity going downstream tends to decrease due to friction with the pipe wall. In order to cope with this, it is said that the inner diameter of the branch pipe from the main pipe to the water supply port or the drain outlet should be sufficiently smaller (preferably 1/3 to 1/6) than the main pipe. Yes. This is because if the fluid resistance of the branch pipe is increased with respect to the main pipe, the difference in loss head due to pipe friction between the upstream and downstream of the main pipe is relatively reduced.
JP 05-340570 JP2002-22382 JP-A-2005-290848 JP 2004-225972 A

  The distributor of the system of the above cited document 2 has a shape in which a large number of through holes are formed in the peripheral wall of a large-diameter cylindrical distributor closed at both upper and lower ends, and the variation in the flow rate of water between the distributors is reduced. However, there is a difference in flow velocity between the portion where the through hole is formed and the portion where the through hole is not formed around one distributor, so that sufficient uniformity of the flow velocity cannot be obtained. In addition, since it has a special shape not found in general-purpose products, there is a problem in terms of manufacturing cost. Furthermore, since the flow path cross-sectional area is reduced at the end of the water passage from the main pipe to the distributor, the flow velocity increases compared to the location slightly upstream from the end, and water is gradually supplied so as not to disturb the temperature stratification. It was the composition which still leaves the problem regarding the request.

  Here, in order to prevent the flow path cross-sectional area from being reduced, it is also conceivable that the entire circumference of the distributor is an opening, except for the connecting portion between the top plate and the bottom plate of the distributor, for example. However, by doing so, the fluid resistance in the branch path (flow path formed by the branch pipe and the distributor) in the water supply path is relatively smaller than the fluid resistance in the main pipe. In other words, the specific gravity of resistance when passing through the main pipe out of the fluid resistance from the main pipe to each distributor increases, so that the pressure loss until water reaches the distributor upstream of the main pipe and the downstream of the main flow The difference from the pressure loss until reaching the distributor is increased. If it becomes so, the merit of patent document 2 that the supply amount between each distributor can be made uniform will be lost. Therefore, it is desired to reduce the flow velocity by a method other than the technique of drilling holes in the wall plate (orifice plate).

  The first object of the present invention is to provide a flow for water supply or drainage of a temperature stratified heat storage tank capable of realizing a flow having a sufficiently low flow velocity and high uniformity of flow velocity distribution even around one distributor or water collector. Providing the end structure of the path.

  The second object of the present invention is to provide a terminal structure of a water supply or drainage channel that can be manufactured at a low cost by combining versatile materials.

  A third object of the present invention is to provide a temperature-stratified heat storage tank having a water supply or drainage channel including the terminal structure.

The first means is
An end structure of a water supply or drainage channel formed to be usable as a distributor mode or a water collector mode on a branch pipe extending from a main pipe piped inside or outside a temperature stratified heat storage tank,
At least one tip 10a of one branch pipe 10, and
Formed by a head member 14 connected to the tip of the branch pipe,
The head member 14 is a hollow body in which the tip 10a of the branch pipe 10 is connected to one of the upper part and the lower part, and the opening 28 is formed in the other, and the water passage 20 extending from the tip 10a to the opening 28 is provided. Including
The water flow path 20 is a single flow path except for the vicinity of the tip 10a of the branch pipe, and the cross-sectional area of the flow path is minimized at the continuous port with the tip of the branch pipe and maximized at the opening 28. Formed as
Further, a speed reduction means 34 is provided in the water passage 20, and this speed reduction means exists downstream in the distributor mode of the pressure loss due to the flow path cross-sectional area expansion e ₁ . It is formed by a combination of frictional resistance associated with the bend of the flow path c ₁ .

    In this means, as a terminal structure of the water supply / drainage channel of the thermal stratification type heat storage tank, the flow channel cross-sectional area is the minimum on the base end side (branch pipe side) and the front end side (opening side) ), Which has a speed reduction means that combines the expansion of the flow path cross-sectional area and fluid friction. The reason for this configuration is as follows.

    First, the single flow path is formed by the flow rate of the branched flow path branched from one base end to a plurality of distal ends as in the above-mentioned Patent Document 2 due to uneven structure and shape of the branch portion. This is because a variation occurs.

    Second, the reason why the cross-sectional area of the flow path is minimized on the proximal end side and maximized on the distal end side is to naturally reduce the flow velocity. In general pipe mechanisms, an orifice is provided near the end of the pipe to limit the flow rate, and the flow path is squeezed. End up. Thereby, the area on the front end side of the flow path is maximized so as not to disturb the temperature stratification.

    Thirdly, the reason for combining the expansion of the flow path cross-sectional area and the fluid friction due to the bending of the flow path as the speed reduction means is that it is necessary to reduce the flow speed to a low speed (preferably 25 to 50 mm / s). is there. A technique for slowing down the water flow by expanding the cross-sectional area of the channel (for example, a depressurization method) has been conventionally known (Patent Document 3). However, compared with such a speed reduction technique, the present invention has a very uniform water velocity distribution. The aim is to supply slowly. The fluid resistance has an element that depends on the shape of the channel (shape resistance) and an element that depends on the viscosity (viscosity resistance). When the Reynolds number is large, the shape resistance is dominant, but the Reynolds number is small. As it becomes, the contribution of viscous resistance increases. Therefore, the flow velocity energy is deprived by the shape resistance due to the enlargement of the cross-sectional area of the flow path in the upstream part where the flow velocity is large in the water passage, and the viscous resistance is increased by bending the flow path on the downstream side. A two-step process of killing provides sufficient deceleration.

    The fact that the flow path bends after the expansion of the flow path, for example, is the same as that of the distributor of Patent Document 2, but it is meaningful to do so at least in the flow path that is largely open at the end. This is because when the opening at the end is narrowed, the flow velocity at the bent portion in the middle of the flow path is reduced as compared with the end portion of the flow path, and the de-energizing effect due to fluid friction is reduced.

    “Distributor mode” refers to the state used as a distributor, and “water collector mode” refers to the state used as a water collector. Here, the “distributor” means a mechanism (distributor) having a function of a water supply port for supplying water to various places of the heat storage tank through a plurality of branch pipes from the water supply main pipe. It is a mechanism that serves as a recovery port for recovering water from various locations of the heat storage tank to the drainage main pipe through a plurality of branch pipes. The biggest difference is whether it is attached to the flow path on the water supply side or the drainage side, and may be the same structurally. In general, a thermal stratification type heat storage tank has a flow path (pipe) connected to the outside of the tank at the upper and lower parts of the tank, depending on whether the heat storage tank is used for cold water heat storage or hot water heat storage. In addition, the roles of the water supply channel and the drainage channel are usually switched between the heat storage operation and the heat radiation operation. Therefore, in the following description, the case where the end structure of the flow path is used for water supply will be described.

  The “tip portion of the branch pipe” is an end portion of the branch pipe opposite to the main pipe, and is a portion having a certain length in the pipe axis direction. As will be described later, when the branch pipe enters into the head member, this entry is the tip of the branch pipe. The tip of the branch pipe may be connected horizontally to the head member or may be provided in the vertical direction. The reason why the distal end portion of the branch pipe is included in the end structure of the flow path according to the present invention is that the distal end portion of the branch pipe contributes to the direction of the water flow in the head member and the like.

  The “head member” is a hollow portion at the end of the flow path that expands in a head shape. This is because the channel cross-sectional area can be enlarged by doing so. “Hollow” means that there is a space for forming a flow path in the interior, and the interior is not limited to a completely “garland”. The structure which has the flow-path formation element for partitioning the space may be sufficient. This is because partitioning the space can increase the flow path length and efficiently reduce the water flow.

  The “water channel” is a single channel formed in the head member and has a function of reducing the water flow. The reason for the “single flow path” is to prevent the flow velocity from changing depending on the location at the opening where the water flow enters the tank. What once merges again is included in a single flow path. For example, when the flow path forming element is installed in the head member, the flow may be blocked by a material that supports this element (in the preferred embodiment, the tip of the branch pipe that supports the small-diameter cylindrical portion). The path is also included in the single flow path.

    "Deceleration means" is means for depriving the flow of kinetic energy by fluid resistance. For example, even when the flow path is gradually expanded while preserving kinetic energy in the middle of the flow, the flow is slowed by a continuous equation (flow path cross-sectional area x flow velocity = constant). For the purposes of the present invention, it is meaningless because the water supply speed is the same if the flow path cross-sectional areas of the water are the same. The speed reduction means of the present invention is a combination of pressure loss due to expansion of the cross-sectional area of the flow path and frictional resistance due to the bending of the flow path. The former mainly has the characteristic of shape resistance, and the latter mainly has the characteristic of viscous resistance. Therefore, by combining the two, a sufficient de-energizing effect can be obtained not only on the upstream side of the high flow rate but also on the downstream side of the low flow rate.

    “Enlarging the channel cross-sectional area” can be a discontinuous expansion of the channel cross-sectional area or a rapid expansion of the channel cross-sectional area. As an example of the enlarged portion of the flow path, the tip of the branch pipe can be cited, and the flow path is expanded from the tip portion into the head member. Since it is conventionally known to use the pressure loss due to the enlargement of the cross-sectional area of the flow path as the depressing means, further explanation is omitted.

  “Friction resistance due to bending of the flow path” is intended to increase resistance by bringing water into contact with the interface using centrifugal force at the bending portion. The temperature stratification type heat storage tank is designed to suppress the flow rate at the stage where the flow flows into the branch pipe, so even if it is not at a level where it can be sent directly to the heat storage tank downstream of the enlarged portion of the flow path, Is quite low. Lowering the flow rate is desirable for a temperature stratified heat storage tank, but on the other hand, it also means that the effectiveness of the speed reduction means due to frictional resistance is reduced. Therefore, the slow flow that has slowed down after passing through the enlarged portion of the flow path is made to enter the bent portion, and the friction between water and the interface is increased by using centrifugal force instead of the pressure loss due to the enlarged flow path.

    In this case, what is important is that the flow velocity gradually decreases immediately before the flow channel expansion point (high flow velocity) → at the flow channel bending portion (medium flow velocity) → at the opening (low flow velocity). The flow path is configured as described above. If the flow velocity is small, such as high flow velocity → low flow velocity → in the middle of the flow velocity, the centrifugal force also becomes small, so that the frictional action at the bending portion is not sufficient. In particular, it is desirable that there is no portion having a narrow channel cross-sectional area downstream of the bent portion of the flow path as compared with the flow path portion at the end of the bend. Further, the water passage may be expanded stepwise a plurality of times, and a curved portion of the flow passage may be provided next to the enlarged portion of the flow passage in each step.

The second means includes the first means, and, of the flow path forming surface that defines the water passage 20, the outer portion of the bent portion of the water passage has a frictional action as compared to its surroundings. A large resistance portion 38 is formed along the flow path forming surface.

  With this configuration, the deceleration effect due to frictional resistance can be enhanced. The “outer portion of the curved portion” is a portion outside the center of the curved portion of the streamline in the wall forming the flow path.

    The “resistive portion” is a portion with high friction provided along the formation surface of the flow path. It is also possible to form the flow path forming surface as a rough surface with a large coefficient of friction (paste a sheet with a large coefficient of friction, etc.). The frictional resistance can be increased by colliding the water flow.

The third means has the first means or the second means, and is formed along the flow path forming surface of the water passage through the friction layer 42 formed of a water-permeable fiber lump.

  In this means, it is proposed that the flow rate of the relatively fast water near the flow path forming surface of the water passage is reduced by the friction layer of the fiber mass. In general, a fluid flowing near an object tends to flow along the surface of the object, but even in the experiment conducted by the applicant, the flow velocity near the flow path forming surface is larger than the place away from the flow path forming surface. This has been confirmed (see FIGS. 18 to 21). That is, the water flow quickly reaches far away in the vicinity of the wall surface forming the flow path. This is a phenomenon that occurs when the flow velocity is a slow water flow of about 25 mm / s, for example, and is different from a general pipe flow with a high flow velocity. Therefore, this means proposes that the slow water flow is more effectively decelerated by forming a friction layer made of fiber mass along the flow path forming surface. Such a fiber lump is known as a water flow filter or the like, but the point of the present invention is that a friction layer of the fiber lump is provided along a flow path forming surface having a relatively high flow rate in a low-speed flow. The friction layer may be provided as a resistance portion at a bent portion of the water passage, but may be formed at a portion other than the bent portion.

  A “fiber lump” is a fibrous body having a certain regularity and having a gap enough to allow water to easily pass through, and has a frictional resistance. A suitable material is a highly durable synthetic resin (for example, vinyl chloride). This fiber lump (or fiber body) may have basically the same structure and material as those used for general purposes as a filter for purifying water tanks and kitchen scourers. The present invention is novel in that this type of fiber mass is used for the purpose of fluid friction resistance. The filter may be fine-grained depending on the purpose of use in order to remove impurities in the fluid. However, in the present invention, a filter with relatively coarse eyes (thick fibers and many gaps) should be used. desirable. When it is installed in an underground pit of a building which is a preferred example, it is difficult to perform maintenance frequently. Further, in order to prevent the fibers from being loosened in the water flow, it is desirable that the fiber mass is a lock material. This point will be described in detail in the column of the embodiment.

  A “friction layer” is one that produces resistance to a fluid primarily within the layer. It is different from a normal rough surface that is merely irregularities on the interface. Strictly speaking, resistance is a combination of shape resistance and viscous resistance, and is not merely fluid friction. In this means, it is an idea that it is not a part of a wall forming the flow path but a flow path, that is, a part of a water passage (see FIG. 10 of the present application). According to an experimental example to be described later, the vertical velocity distribution of the opening in a test body that does not use a fiber lump is considerably different from 10 mm / sec at the center and up to 35 mm / sec at the outer periphery. This is considered to be because the outer side becomes faster than the inner side at the bent portion, and the fast flow outside this side is maintained as it is along the flow path forming surface (in the illustrated example, the inner surface of the large-diameter cylindrical portion) up to the opening. Therefore, a friction layer is installed in the outer portion of the curved portion corresponding to the high-speed portion of the flow path, and the high-speed flow is pushed into the friction layer by centrifugal force so as to reduce the speed difference from the inside of the flow. Therefore, it is considered that the friction effect is larger when the thickness of the friction layer is larger to some extent. The thickness is set according to the flow path width and flow velocity at the bent portion. In the illustrated example described later, a friction layer having a thickness of 25 mm is provided at a bent portion having a width of about 75 mm.

The fourth means includes the first means to the third means, and the water passage 20 has a portion where the flow passage cross-sectional area rapidly increases from the distal end portion 10a of the branch pipe toward the opening portion 28. In addition, the flow path is configured to be repeatedly bent or curved.

  In this means, the centrifugal force at the bent portion can be increased by folding the flow path 180 degrees, and the frictional action can be enhanced. As a manner of folding, a folding back in a parallel layer shape or a folding back in a concentric tube shape in the inner and outer directions can be considered.

The fifth means includes the fourth means, and the water flow path 20 includes a plurality of mutually overlapping flow path portions 20a, and is formed so as to be folded from one flow path portion to the next flow path portion. And
These flow channel portions are folded concentrically from the inside to the outside with the first one flow channel portion formed in a column shape as the center.

    In this means, the flow path portion is folded concentrically so that a uniform flow velocity distribution in the circumferential direction can be realized. For example, if the width of each cylindrical flow path portion is constant, the area of the flow path portion outside the inner flow path portion becomes larger due to the difference in diameter, and a water flow path that expands the flow path in steps is easily realized. can do.

The sixth means includes third means or fourth means, and the head member 14 includes:
A horizontal outward flange-like wall 48 attached to the tip of the branch pipe 10 extending in the vertical direction;
A cylindrical wall 50 protruding in the same direction as the branch pipe from the outer edge of the outward flange-shaped wall;
A support rod 52 protruding from the inside of the main pipe 8 through the branch pipe 10 into the cylindrical wall 50;
A baffle plate 54 attached to the upper end of the support bar and extending toward the inner surface of the cylindrical wall with a certain gap between the outward flange-like wall 48,
The support bar 52 extends along the axis of the branch pipe so as not to touch the inner surface of the branch pipe,
The distance L ₁ between the outer surface of the support bar 52 and the inner surface of the branch pipe 10 and the distance L ₂ between the outer edge of the baffle plate 54 and the inner surface of the cylindrical wall 50 are constant in the circumferential direction.

  The technique of providing a baffle plate for changing the blowing direction in the vicinity of the fluid blowing port is conventionally known (for example, Patent Document 4). In this means, a branch corresponding to the blowing port is formed inside the cylindrical head member. It has been proposed to extend the baffle plate to the tube wall side beyond the tube tip opening. As a result, the flow line bends in the vertical-horizontal-vertical direction in the tip of the branch pipe, through the gap between the outward flange-like wall and the baffle plate, and the three flow passage portions of the outer edge of the baffle plate and the inner surface of the cylindrical wall. Designing. As described above, the centrifugal force at the bent portion is smaller than the case of bending at 180 degrees, but the configuration can be made relatively simple. The three channel portions may be configured such that the channel cross-sectional area gradually increases. In addition, it is preferable to design the branch pipe so that the pipe axis of the branch pipe and the cylinder axis of the cylinder wall coincide with each other in order to make the flow path distribution uniform in the circumferential direction.

The seventh means is
A branch pipe extending from a main pipe piped inside or outside the temperature-stratified heat storage tank is provided so as to be usable in a distributor mode or a water collector mode. At least one branch pipe tip and a tip of the branch pipe A terminal structure of a water supply or drainage channel formed by a head member connected to a portion,
The head member 14 is
A tall large-diameter cylindrical portion 16 having one of the upper and lower end faces as an opening 28 and the other closed;
A low-profile, small-diameter cylindrical portion 18 that closes one of the upper and lower end faces and has the other communicating port 24;
A hollow formed by concentrically inserting the small diameter cylindrical portion 18 into the back of the large diameter cylindrical portion 16 so that the closed end of the large diameter cylindrical portion 16 and the communication port 24 of the small diameter cylindrical portion 18 face each other. Body,
The distal end portion 10a of the branch pipe 10 is inserted through appropriate positions of the large diameter cylindrical portion 16 and the small diameter cylindrical portion 18,
A water passage 20 is formed from the tip portion to the inside of the small-diameter cylindrical portion and through the gap between the cylindrical walls of the small-diameter cylindrical portion and the large-diameter cylindrical portion to the opening 28.

    This means is that, among the ideas described in the first means, the expansion of the channel cross-sectional area and the bending (turning back) of the channel existing downstream in the distributor mode at the location where the channel cross-sectional area is enlarged. It proposes a specific measure to be realized. In this means, since the head member is combined with common general-purpose elements such as large and small cylindrical portions, it can be easily manufactured. The tip of the branch pipe that has entered the head member can be used as a means for guiding the water supply into the small-diameter cylindrical portion and at the same time as a means for supporting the small-diameter cylindrical portion. The branch pipe may enter from the side of the head member or may enter from the vertical direction. The number of branch pipes that enter the head member is not limited to one, and may be two or more. What has been described in the preceding means (for example, the friction layer) can be incorporated into this means unless technically contrary to the contents of this means. The friction layer is formed not only at the bent portion of the water passage, but also over the entire length of the tube length or any part of the tube length among the tube wall inner surface of the large diameter tube portion and the tube wall inner surface of the small diameter tube portion. can do.

The eighth means includes the first means to the seventh means, and the portion of the head member 14 opposite to the opening 28 is filled with water in the heat storage tank 2 or the heat storage tank 2. There is provided a valve mechanism 60 for draining and venting air that opens when water is sucked from the air and closes when heat is stored or released.

  This means proposes a mechanism for draining or bleeding air from the head member. In general, the amount of water in the heat storage tank is often constant, and it is not necessary to drain water or vent the air in normal operation.However, when water is poured into the heat storage tank for the first time, A situation may occur where air does not escape from the head member even though it is filled. Recently, water in the heat storage tank has also been used as fire extinguishing water, and when water for fire extinguishing is taken, the water level in the heat storage tank drops rapidly, so there is no water outside the head member. A situation can occur where water remains in the head member. In either case, a large load is applied to the head member. In order to avoid this, a valve mechanism for draining or bleeding air is provided.

  In order to realize this valve mechanism, normal operation in which the inside and outside of the head member is filled with water using a “floating” type valve body that is lighter than water and a “weight” type valve body that is heavier than water. At the time of heat storage (heat storage and heat dissipation), the valve seats pierced in the head member are permanently blocked by the buoyancy or load, but during the water injection or water discharge, the valve bodies are detached from the valve seats due to the water level. It is recommended that air can enter and exit.

  Specifically, in the head member having an upper surface opening, a water drain valve and an air vent valve are respectively provided as shown in FIGS. The drain valve uses the upper part of the valve cylinder penetrating the bottom wall of the head member as a valve seat, and holds the floating valve body in the valve cylinder so as to be movable up and down. The air vent valve may be configured such that a lower part of a valve cylinder penetrating the bottom wall of the head member is used as a valve seat, and a valve body heavier than water is held up and down freely. Further, as shown in FIGS. 14D to 14F, the head member having the lower surface opening is provided with a valve for both draining and bleeding. In this valve, an upper portion of a valve cylinder penetrating the top wall of the head member is used as a valve seat, and a valve body floating in the valve cylinder is held up and down freely. These configurations will be described in detail in the embodiment section.

The ninth means is
A water supply main pipe 8 is connected to one of the upper and lower parts of the tank, and a drain main pipe 8 is connected to the other, and a distributor E _{1 is connected} to the tip of the branch pipe 10 from the water supply side main pipe 8, and the drain side main pipe 8 is connected. at a temperature stratified storage tank comprising a water collecting unit E ₂ is attached respectively to the tip of the branch pipe 10 from,
The distributor E ₁ and the water collector E ₂ have a terminal structure of a water supply or drainage channel according to any one of claims 1 to 8,
Of the openings 28 of the distributors E _{1 to} E ₂ , those that are connected to the lower main pipe 8 face downward toward the bottom of the heat storage tank 2, and those that are connected to the upper main pipe 8 are those of the heat storage tank 2. It is oriented upward facing the top surface.

    In this means, a temperature stratified heat storage tank including the above-described channel end structure is proposed. The flow rate is reduced by making the lower opening face the bottom surface of the heat storage tank and the lower opening face the upper end face of the heat storage tank. The heat storage tank can be a multi-tank connection type heat storage tank.

The invention according to the first means has the following effects.
O Since the water flow path 20 is a single flow path, the flow speed is not easily controlled at each branch portion as in the case of a plurality of branched flow paths, and the speed distribution can be easily controlled.
○ Since the water flow channel 20 is formed so that the cross-sectional area of the flow channel is minimized at the continuous port with the tip of the branch pipe and maximized at the opening portion 28, the outflow speed can be suppressed during water supply, thereby reducing the low water depth. A temperature stratified heat storage tank can be realized using this tank.
○ Since the speed reduction means combines the expansion of the cross-sectional area of the flow path and the fluid friction downstream of the expanded portion, it effectively exerts a depressurizing action on both the upstream side of the high flow rate and the downstream side of the low flow rate.
O Centrifugal force at the curved portion of the flow path is used to reduce fluid friction as a speed reduction means, so that it is possible to effectively reduce the flow that has become slow due to the expansion of the flow path.

The invention according to the second means has the following effects.
O Since the resistance portion having a larger frictional action than the surroundings is provided on the outer portion of the bent portion, the frictional force is increased by effectively utilizing the centrifugal force, and the deceleration can be effectively performed.
○ Since the resistance part is along the flow path formation surface, it does not disturb the flow and is suitable for creating a slow flow with high homogeneity.

  According to the invention relating to the third means, since the friction layer formed by the fiber mass is formed along the flow path forming surface of the water channel, a dynamic depressing action can be obtained as compared with a normal rough surface.

  According to the fourth aspect of the invention, after the deceleration by the rapid expansion of the flow path, the fast flow portion at the bending portion is pressed against the inner wall surface by centrifugal force, so that the kinetic energy can be more effectively obtained. I can take it away.

The invention according to the fifth means has the following effects.
○ Friction effect using centrifugal force increases because it is folded.
○ Since it is folded back in an annular shape, it is easy to design the channel cross-sectional area of the second and subsequent channel parts larger and narrower the channel width than the first channel part. Enough can be secured.
○ Because it is concentric, it is possible to reduce the variation in flow velocity distribution in the same flow path plane cross section.

The invention according to the sixth means has the following effects.
Since the baffle plate 54 is attached to the tip of the support rod 52 protruding from the branch pipe, it can be designed as a complete single flow path in which the flow path is not partitioned from the branch pipe 10 to the tip of the cylindrical wall 50.
○ The distance between the branch pipe and the support rod, the distance between the outer edge of the baffle plate 54 and the inner surface of the cylindrical wall 50 are made constant in the circumferential direction, and the baffle plate 54 and the outward flange-like wall are made constant. Can ensure a high level of uniformity.

    According to the seventh aspect of the invention, since the large and small cylindrical portions are the main members, it can be manufactured by combining general-purpose materials distributed in the market, and the manufacturing cost can be reduced. .

  According to the eighth aspect of the invention, the valve mechanism 60 for draining or bleeding is provided, so that the periphery of the head member is filled with air and filled with water, or conversely, the surrounding is filled with water. Can be prevented from applying unnecessary load to the main pipe and the branch pipe.

According to the ninth aspect of the invention, among the openings 28 of the distributors E _{1 to} E ₂ , the ones connected to the lower main pipe 8 face the bottom surface of the heat storage tank 2 and face the upper side downward. Since the pipe connected to the main pipe 8 is oriented upward facing the upper end surface of the heat storage tank 2, the lower surface and the upper surface (or water surface) of the heat storage tank 2 are replaced with a flow path regulating plate (baffle plate), and water. The flow of water can be made horizontal, the water depth of the tank can be lowered, and the configuration can be simplified.

  FIG. 1 to FIG. 8 show the terminal structures of the temperature stratified heat storage tank and the water supply / drainage channel according to the first embodiment.

  In FIG. 1, 2 is a temperature-stratified heat storage tank, 4 is a heat exchanger, and 6 is a water supply / drainage channel.

  The temperature stratification type heat storage tank 2 is a tank whose upper end is closed. The illustrated one is a multi-tank connection type, but may be a single tank type. This heat storage tank can be constructed using the basic pit of an existing building. Although omitted in the drawing, a through hole is provided in the upper wall of the heat storage tank.

  The heat exchanger 4 supplies heat generated by a heat source to the heat storage tank during the heat storage operation, and supplies heat extracted from the heat storage tank to the outside during the heat dissipation operation.

  The water supply / drainage channel 6 is configured between the temperature-stratified heat storage tank 2 and the heat exchanger 4, and the main pipe 8 of the water supply path 6A is at the lower part of the tank, and the main pipe 8 of the drainage channel 6B is at the upper part of the tank. Each has a piping. In the drawings, P is a heat storage / heat dissipation pump, and V is a flow path switching valve.

  In each main pipe 8, a branch pipe 10 is intermittently extended from upstream to downstream, and a distributor and a water collector are formed as a terminal structure 12 of each flow path. In the illustrated example, a pair of branch pipes extend from each location of the main pipe.

  This end structure 12 is formed of at least a tip portion 10 a of the branch pipe and a head member 14. FIGS. 2 and 3 show the end structure of the upper main pipe, and FIGS. 4 and 5 show the end structure of the lower main pipe, respectively. Therefore, the configuration will be described below by taking the terminal structure of FIGS. 2 and 3 as an example.

  The head member 14 has a large-diameter cylindrical portion 16 with a bottom and a small-diameter cylindrical portion 18 with a top, and the small-diameter cylindrical portion is disposed in the back (or lower half) of the large-diameter cylindrical portion 16. Has been. The distal end portions 10a of the pair of branch pipes are inserted into the small diameter cylindrical portion through the lower left and right side walls of the large diameter cylindrical portion 16 and the left and right side walls of the small diameter cylindrical portion. These branch pipes also serve as means for supporting the small-diameter cylindrical portion. The large-diameter cylindrical portion 16 and the small-diameter cylindrical portion 18 are straight cylindrical shapes having a constant inner diameter and outer diameter in the vertical direction, and are cylindrical shapes arranged concentrically as viewed from above. By doing in this way, the water flow path 20 from the inside of a small diameter cylinder part to the opening part of a large diameter cylinder part through the clearance gap between both cylinder parts is formed.

    In the illustrated example, the distal end portion 10a of the branch pipe is attached to the head member as a separate part from the remaining portion of the branch pipe to form a terminal structure as one unit. The remaining portion of the branch pipe can be fitted to the tip of the branch pipe.

  The small diameter cylindrical portion 18 has a lower end surface as a communication port 24 to the large diameter cylindrical portion. A partition wall 26 perpendicular to the axial direction of the branch pipe tip is provided inside the small-diameter cylindrical portion, and is opposed to the branch pipe tip surface so that running water from the tip of the branch pipe hits both surfaces of the partition wall.

  The large-diameter cylindrical portion 16 has an upper end surface as an opening 28 into the heat storage tank. Further, an appropriate number of support portions 30 are attached to the outer surface of the cylindrical wall, and the head member 14 can be suspended in the heat storage tank by hanging a chain on the support portion, for example. However, the support method can be changed as appropriate. Further, in the large-diameter cylindrical portion 16, a water flow filter 32 made of a fiber mass traverses the passage portion downstream of the gap between the large-diameter cylindrical portion and the small-diameter cylindrical portion, in the illustrated example, in the upper portion of the small-diameter cylindrical portion. Is installed side by side. The fiber mass is preferably made of a synthetic resin, and the water filter can be formed of vinyl chloride. In order to support the fiber water filter, a support material (for example, a mesh plate) may be installed in the large-diameter cylindrical portion.

  In this embodiment, the water flow path 20 includes an upstream portion 20a that folds outward from the inside of the small-diameter cylindrical portion, a midstream portion 20b between the cylindrical walls of the small-diameter cylindrical portion and the large-diameter cylindrical portion, and an upper portion above the large-diameter cylindrical portion. And a downstream portion 20c. And the upstream part 20a is made to produce the frictional effect by a centrifugal force in the bending location 22 which curves outside from a communicating port. In the illustrated example, the channel cross-sectional area of the midstream portion 20b (the cross-sectional area of the gap between the small diameter cylindrical portion and the large diameter cylindrical portion) is slightly larger than the channel cross sectional area in the small diameter cylindrical portion of the upstream portion 20a. Compared to 20b, the flow path cross-sectional area of the downstream portion 20c is larger. In this way, the water passage is expanded in stages from upstream to downstream without being involuntarily constricted on the way.

  The end structure of the upward opening in FIGS. 4 and 5 is slightly different from the position of the support portion in comparison with that of the downward opening.

In the above configuration, when flowing into the small-diameter cylindrical portion from the distal end portion 10a of the branch pipe, the flow of water as shown in FIG. 6 causes the flow path enlargement e ₁ at the front end of the branch pipe to bend the flow path due to the collision with the partition wall. c ₁ → channel expansion e ₂ at the communication port e ₂ → bending c ₂ at the curved portion 22 → flow path expansion e ₃ at the end of the midstream portion toward the opening. Thereby, the deceleration means 34 is comprised. Further, the flow velocity at the outer portion of the flow is higher at the bent portion 22 than at the inner portion, and according to the applicant's experiment, the speed difference between the outer portion and the inner portion of the bent portion 22 remains in the velocity distribution at the opening 28. There is a tendency to appear. Therefore, in the illustrated example, the large-diameter cylindrical portion is a bottomed cylindrical shape, and the corner portion 40 between the bottom plate and the cylindrical wall is a resistance portion 38. That is, the collision of the flow with the corner 40 increases the frictional action, suppresses the speed of the outer portion of the flow, and reduces the variation in the flow path distribution.

  FIG. 7 shows a modified example of the first embodiment, in which the speed of the inner portion of the flow at the bent portion is increased by rounding the corner of the small-diameter cylindrical portion.

    FIG. 8 shows the operation of this embodiment. FIG. 8A shows the cold water heat storage time and FIG. 8B shows the cold water heat release time.

  At the time of cold water heat storage, a pipe in which both ends of the upper portion of the heat exchanger 4 are omitted in FIG. 1A is connected so as to form a circulation path between a cold heat source (not shown) and a heat transfer medium. The heat transport medium generated and transported by the cold heat source is heat-exchanged with the cold water in the circulation path on the heat storage tank side via the heat exchanger 4. On the heat storage tank side, through the water supply flow path 6A including the lower main pipe and the branch pipe, the end structure that opens below the tank and opens toward the bottom is used as a distributor. The heat-exchanged cold water is supplied into the tank and stored. At the same time, from the inside of the tank to the heat exchanger 4 via the drainage flow path 6B including the upper main pipe and the branch pipe, with the terminal structure existing above the inside of the tank and opened toward the upper surface as a water collector. Refluxed.

    When chilled water is dissipated, a pipe in which both ends of the upper portion of the heat exchanger 4 are omitted is connected to a heat exchanger on the load side such as an air conditioner (not shown) so as to form a circulation path of the heat transfer medium. . On the load side, the heat transfer medium exchanged with the cold water on the heat storage tank side via the heat exchanger 4 is transferred to the heat exchanger on the load side, and heat exchange is performed on the load side. Refluxed. On the heat storage tank side, it is stored in the tank via the drainage flow path 6B including the lower main pipe and the branch pipe, with the terminal structure existing below the tank and opened toward the bottom as a water collector. The cold water that has been supplied is sent to the heat exchanger 4 to exchange heat with the heat transfer medium on the load side. The cold water heat-exchanged by the heat exchanger 4 passes through the water supply flow path 6A including the upper main pipe and the branch pipe, and the end structure opened upward toward the upper surface in the tank is used as a distributor. Reflux in.

    Other embodiments of the present invention will be described below. In these descriptions, the same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.

    9 and 10 show a terminal structure according to the second embodiment of the present invention.

    In the present embodiment, the bent portion 22 and the midstream portion 20b are more specifically located at locations corresponding to the outside of the bent portion 22 when the small diameter cylindrical portion 18 is folded back into the gap between the small diameter cylindrical portion and the large diameter cylindrical portion 16. A friction layer is formed as the resistance portion 38 on the flow path forming surface of the outer portion.

    This friction layer is formed as a fiber mass having water permeability, preferably made of synthetic resin. The ideal conditions for the material of the friction layer can be explained conceptually. First, the porosity is large enough that the frictional resistance does not become excessive, and secondly, the surface area is large enough to secure a sufficient friction surface, and thirdly distributed. It is a light material for facilitating the support of the water collector or the water collector, and fourthly, it is a material that does not change its properties even when wet with water. In particular, a material having water resistance, in other words, a material having low water absorption is preferable. It is also required that the shape does not collapse when touched by water, that is, has shape retention in a water stream. For this purpose, it is desirable to use a chemical fiber locking material. The lock material is made by curling animal and plant fibers, synthetic resins, etc. into a shape like a curly sheep (lock) as shown in FIG. 10 to form many small elastic bodies, and further bonded and fixed with a binder. Is. Such locks have irregular gaps that are significantly larger than the fiber thickness. For example, a commercially available product having a gap of several mm is known when the fiber thickness is 0.5 mm or less. Thus, the gap forms part of the water channel. That is, as shown in FIG. 10, out of the water flowing from the inside of the small diameter cylindrical portion 18 into the bent portion 22, the water flowing outside the bent portion passes through the friction layer that is the resistance portion 38. In the friction layer, the fibers are randomly crossed and confused, preventing the flow of water. The outer portion of the bent portion 22 should naturally have a higher flow velocity than the inner portion, but the friction layer can reduce the flow velocity at the outer portion and reduce the difference in flow velocity from the inner portion. .

    When attaching the friction layer 42 to the head member 14, the general-purpose material in which the fibers are formed in a plate shape or a layer shape is used with respect to the bottom surface of the large diameter cylindrical portion or the peripheral surface of the lower peripheral wall of the large diameter cylindrical portion. It is sufficient to fix each so as not to be peeled off by water flow. In the illustrated example, the friction layer is formed on both the lower portion of the peripheral wall and the bottom wall of the large-diameter cylindrical portion, but the friction layer may be formed only on one of them as described later.

    In the illustrated example, the friction layer 42 extends beyond the bent portion 22 of the upstream portion 20 a in the water passage 20 and into the midstream portion 20 b between the small diameter cylindrical portion 18 and the large diameter cylindrical portion 16. However, the friction layer 42 may be further extended to the downstream portion 20c, for example, to the opening 38. In the illustrated example, the friction layer is formed only on the large-diameter cylindrical portion 16 in order to make the flow velocity distribution uniform, but the friction layer is formed on the inner surface or the outer surface of the small-diameter cylindrical portion 18 from the viewpoint of lowering the average flow velocity. It may be formed.

    FIG. 11 shows a third embodiment of the present invention. In this embodiment, the branch pipe 10 protrudes from the main pipe 8 in the vertical direction, and a head member 14 is attached to the branch pipe. The head member protrudes from the distal end portion 10a of the branch pipe in the same vertical direction through the outward flange-like wall 48, and the support rod 52 is coaxially formed from the inside of the branch pipe. A horizontal baffle plate 54 is attached to the tip of the support bar.

The distance L ₁ between the support bar and the inner surface of the branch pipe and the distance L ₂ between the outer edge of the baffle plate 54 and the inner surface of the cylindrical wall 50 are constant in the circumferential direction, thereby reducing the variation in the flow velocity distribution.

  Further, a friction layer 42 made of a fiber lump may be provided as a resistance portion on the upper surface of the outward flange-like wall 48 and the inner surface of the cylindrical wall 50.

  12 to 16 show a fourth embodiment of the present invention. In this embodiment, the head member 14 is provided with a valve mechanism 60 for draining and bleeding air. Supplementing what has been described in the means for solving the problems of the invention, when cleaning the water heat storage tank, water is drained via the main pipe and the heat storage / radiation pump. A water heat storage tank and a fire prevention water tank may be used together to save energy, and when a fire breaks out in the surrounding site, there may be a sudden drainage by the fire brigade. In the configuration shown in the previous embodiment, the capacity of the head member is increased in order to suppress the inflow and outflow rates with respect to the water heat storage tank, and therefore, the water level is easily changed during water filling or draining. As shown in FIG. 15 (A), when water is filled, water does not enter the head member, so it receives buoyancy, or when water is drastically drained as shown in FIG. 15 (B), water is drained even if the surrounding water level drops. If the strength of the head member is not sufficient, this may cause damage. This embodiment prevents such a phenomenon.

  FIG. 12 shows a water draining and air venting valve mechanism 60 used for the head member having an upper opening. In this case, the water drain valve 62 and the air vent valve 64 may be provided separately. Each valve has a valve barrel 66 that hangs down through the bottom wall of the head member.

    The drain valve 62 has an upper part of the valve cylinder 66 as a valve seat 68, and holds a valve body 70A functioning as a float lighter than water in the valve cylinder so as to be movable up and down. Means (a locking flange in the illustrated example) for mounting the valve body is attached to the lower part of the valve cylinder. In a state where the valve body 70A is placed, air is passed from above to below. The buoyancy of the valve body 70A is designed so as to be larger than the static pressure of the fluid in the water supply / drainage channel during heat storage / heat radiation.

    The air vent valve 64 has a valve seat 68 at the lower part of the valve cylinder, and holds a valve body 70B functioning as a weight heavier than water in the valve cylinder so as to be freely movable up and down.

    In this embodiment, in order to provide the valve hole of the valve mechanism on the bottom wall of the head member, the formation of the friction layer on the upper surface of the bottom wall is omitted, and the friction layer 42 is provided only around the inner surface of the lower part of the cylindrical wall. Yes. The same applies to the structure shown in FIG.

    FIG. 13 shows a water draining and air venting valve mechanism 60 used for the head member 14 having a lower opening. In this case, it is preferable to provide a single valve for both draining and bleeding. This valve has a valve barrel 66 that stands up through the top wall of the head member. The other structure is the same as the drain valve of FIG. 12, and the upper part of the valve cylinder 66 is used as a valve seat 68, and a valve body 70A that functions as a float that is lighter than water is allowed to move up and down in the valve cylinder. Insert and hold. Next, the operation of the valve mechanism in the upper opening head member will be described.

  As shown in FIG. 14A, when water is filled in the heat storage tank 2, the drain valve 62 of the valve mechanism 60 has the floating valve element 70 </ b> A seated on the valve seat 68 due to the inflow of water into the valve cylinder. In the air vent valve 64, the weight-type valve body 70B is pushed up by water and slightly floats from the valve seat, and in this state, water flows into the head member 14 via the valve cylinder 66. . Thereby, the air in the head member is pushed out.

  As shown in FIG. 14B, during normal heat storage or heat dissipation, the drain valve 62 is closed by the buoyancy of the floating valve body 70A and the air vent valve 64 is closed by the load of the weight type valve body 70B. Thereby, the temperature stratification state in the heat storage tank 2 is maintained.

  At the time of draining shown in FIG. 14C, the floating valve body 70A descends from the valve seat 68 in the drain valve 62, and water is drained.

  Next, the operation of the valve mechanism in the head member having the lower opening will be described.

  At the time of water filling shown in FIG. 14D, air in the head member escapes upward by floating of the floating valve body 70A, whereby water enters the head member.

  During normal heat storage or heat dissipation shown in FIG. 14E, the floating valve body 70A is seated on the valve seat by buoyancy, thereby maintaining the temperature stratification state of the heat storage tank.

  At the time of draining shown in FIG. 14 (F), the valve body 70A is also lowered by the air entering the valve cylinder from the valve seat. Furthermore, when the air enters the head member from the valve cylinder, water in the head member is drained.

FIG. 16 is an example of the present embodiment, and a valve 72 for bleeding air when water is filled is provided.
[Example]
Details of a preferred embodiment of the upward end structure described in FIG. 12 will be described. Since this example was used as a test specimen for an experiment described later, data such as dimensions will be described in detail. As described above, in the structure of FIG. 12, the friction layer 42 is formed only on the inner surface of the lower portion of the peripheral wall of the large-diameter cylindrical portion. As described in Table 1, the vertical length of the friction layer is 100 mm, the thickness is 25 mm, and the porosity is 95%. The reason why the configuration shown in FIG. 12 is selected as the test specimen is to examine how much the resistance effect of deceleration can be expected when the attachment range of the friction layer cannot be made very large.

  Since the test was conducted for the performance test of the end structure of the flow channel shown in the first embodiment of the present invention, the result will be described below.

  FIGS. 17 to 21 show a method and results of an experiment of the flow velocity distribution in the vertical direction at the opening of the head member.

  As shown in FIG. 17 (A), at the opening of the head member, the measurement points 1 to 9 are taken in the direction perpendicular to the direction of the branch pipe, and the measurement points 10 to 17 are taken in the same direction as the branch pipe. It was measured. For the experiment, a speed sensor 82 was attached to the tip of an L-shaped jig 80 as shown in FIG. A speed sensor having a measurement range of ± 100 mm / s and a measurement error of ± 2% / FS was used. The sensor part (speed-sensitive part) has a length of 20 mm and a diameter of 8 mmφ. The position of the opening from the water surface is 96 mm. At that time, each measurement point was measured at intervals of 1 second for 30 seconds, and the average value, minimum value, and maximum value were measured.

  The test was conducted on four cases with varying flow rate conditions and structural conditions. In the first to third cases, the flow rate conditions are the same (the inflows from the left and right are 90 L / min each), and in the first case, the lower fiber mass (friction layer) and the upper fiber mass (passage) A test body having a water filter was used as a test body having a lower fiber mass in the second case, and a test body having no fiber mass was used in the third case. In the fourth case, a test body having no fiber mass was used with the flow rate conditions set to 110 L / min from the left and 70 L / min from the right.

  The data in this table is shown in order to confirm that the flow velocity distribution is sufficiently small in each case and there is no place where the flow velocity is too fast. In terms of numerical values, the average flow velocity is highest in Case 1. However, considering experimental error, it is not a significant difference, and it is not a test in which experimental conditions are adjusted in order to compare fluid resistance between cases. What is important here is that the data in FIG. 18 to FIG. 21 indicate that the flow velocity tends to decrease as it goes to the center of the head member, and the flow velocity tends to increase as it goes outward.

  Further, comparing FIG. 19 showing the result of case 2 (with friction layer + no water passage filter) and FIG. 20 showing the result of case 3 (without friction layer + no water passage filter), the inner edge of the large-diameter cylindrical portion is compared. At measurement points 1, 9, 10, and 17 corresponding to, it can be seen that the flow velocity is lower by about 3 to 5 mm / sec in case 2 at all observation points. This is interpreted that the flow velocity can be reduced in the outer portion of the bent portion 22 of the water passage due to the resistance of the friction layer.

    FIG. 22 to FIG. 26 show a method and results of an experiment of horizontal flow velocity distribution in the vicinity of the opening of the head member.

    As shown in FIG. 22A, in the vicinity of the opening of the head member, the observation points 1 to 8 were taken in the horizontal direction in the radial direction, and the velocity distribution was measured.

    For the experiment, a speed sensor 82 was attached to the tip of an I-shaped jig 80 as shown in FIG. The position of the opening from the water surface is 96 mm, and the position of the sensor from the water surface is 50 mm. In the measurement, each measurement point was measured at an interval of 1 second for 30 seconds, and the average value, minimum value, and maximum value were measured.

  The test was performed for the same four cases as in FIGS.

In this experiment, the following was found.
○ In all cases, the total average flow velocity was 8mm / sec or less, and it flowed out in 8 directions.
○ Compared to Case 1, the fluctuation range of the measurement data (maximum value and minimum value width) is larger, but in most cases, the flow velocity was 8 mm / sec or less.

  23 to 26 show the results of this experiment. In case 1, the average flow velocity in almost all directions was uniform as shown in FIG. In case 2, as shown in FIG. 24 (B), the average flow velocity had a variation of about 5 mm / sec. Even in case 3, there is a slight variation in the average flow velocity as shown in FIG. In case 4, as shown in FIG. 26 (B), the average speed is substantially uniform, but the fluctuation of the flow velocity at each measurement point is large.

1 is an overall configuration diagram of a temperature stratified heat storage tank according to a first embodiment of the present invention. It is a top view of the thing of an upper opening among the terminal structures of the flow path of the thermal storage tank of FIG. It is a longitudinal cross-sectional view of the terminal structure of FIG. It is a top view of the thing of a downward opening among the terminal structures of the flow path of the thermal storage tank of FIG. It is a longitudinal cross-sectional view of the terminal structure of FIG. It is a longitudinal cross-sectional view of the principal part of the terminal structure of FIG. It is a longitudinal cross-sectional view of the principal part of the modification of the terminal structure of FIG. It is operation | movement explanatory drawing of the thermal storage tank of FIG. It is a longitudinal cross-sectional view of the terminal structure of the temperature stratification type heat storage tank which concerns on the 2nd Embodiment of this invention. FIG. 10 is an enlarged view of a main part of the terminal structure of FIG. 9. It is a longitudinal cross-sectional view of the terminal structure of the temperature stratification type heat storage tank which concerns on the 3rd Embodiment of this invention. It is a longitudinal cross-sectional view of the terminal structure of the upper opening of the temperature stratification type heat storage tank which concerns on the 4th Embodiment of this invention. It is a longitudinal cross-sectional view of the terminal structure of the downward opening of the temperature stratification type heat storage tank concerning the embodiment. It is operation | movement explanatory drawing of the principal part of the temperature stratification type heat storage tank which concerns on the same embodiment. It is operation | movement explanatory drawing of the principal part of the temperature stratification type heat storage tank which concerns on the same embodiment. It is an Example of the same embodiment. It is explanatory drawing of the experiment example conducted about 1st Embodiment of this invention. It is a figure showing the result of the 1st case of this experiment. It is a figure showing the result of the 2nd case of this experiment. It is a figure showing the result of the 3rd case of this experiment. It is a figure showing the result of the 4th case of this experiment. It is explanatory drawing of the other experiment example conducted about 1st Embodiment of this invention. It is a figure showing the result of the 1st case of this experiment. It is a figure showing the result of the 2nd case of this experiment. It is a figure showing the result of the 3rd case of this experiment. It is a figure showing the result of the 4th case of this experiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 2 ... Temperature stratification type thermal storage tank 4 ... Heat exchanger 6 ... Flow path for water supply / drainage 6A ... Flow path for water supply 6B ... Flow path for drainage 8 ... Main pipe 10 ... Branch pipe 10a ... End part 12 ... End structure 14 ... Head member DESCRIPTION OF SYMBOLS 16 ... Large diameter cylinder part 18 ... Small diameter cylinder part 20 ... Water flow path 20a ... Upstream part 20b ... Middle flow part 20c ... Downstream part 22 ... Curved part 24 ... Communication port 26 ... Septum 28 ... Opening part 30 ... Support part 32 ... Water flow Filter 34 ... Deceleration means 38 ... Resistance part 40 ... Corner part 42 ... Friction layer 48 ... Outward flange-like wall 50 ... Cylindrical wall 52 ... Support bar 54 ... Baffle plate 60 ... Valve mechanism 62 for draining and venting water Valve 64 ... Air bleeding valve 66 ... Valve barrel 68 ... Valve seat 70A, 70B ... Valve element 72 ... Valve
74 ... Water supply pipe 75 ... Drain pipe 80 ... Jig 82 ... Speed sensor E ₁ ... Distributor E ₂ ... Water collector v ... Flow path switching valve p ... Heat storage / radiation pump
e ₁ ... Expansion of the cross-sectional area of the channel c ₁ ... Bending of the channel

Claims (9)

An end structure of a water supply or drainage channel formed to be usable as a distributor mode or a water collector mode on a branch pipe extending from a main pipe piped inside or outside a temperature stratified heat storage tank,
At least one tip 10a of one branch pipe 10, and
Formed by a head member 14 connected to the tip of the branch pipe,
The head member 14 is a hollow body in which the tip 10a of the branch pipe 10 is connected to one of the upper part and the lower part, and the opening 28 is formed in the other, and the water passage 20 extending from the tip 10a to the opening 28 is provided. Including
The water flow path 20 is a single flow path except for the vicinity of the tip 10a of the branch pipe, and the cross-sectional area of the flow path is minimized at the continuous port with the tip of the branch pipe and maximized at the opening 28. Formed as
Further, a speed reduction means 34 is provided in the water passage 20, and this speed reduction means exists downstream in the distributor mode of the pressure loss due to the flow path cross-sectional area expansion e ₁ . A terminal structure of the water supply or drainage flow path of the temperature stratified heat storage tank, characterized by being formed by a combination of frictional resistance associated with the flow path bend c ₁ .   Among the flow path forming surfaces that define the water flow path 20, a resistance portion 38 having a larger frictional action than that of the periphery is formed along the flow path forming surface on the outer portion of the bent portion 22 of the water flow path. The terminal structure of the water supply or drainage channel of the temperature stratified heat storage tank according to claim 1,   The water supply or drainage channel of the temperature stratified heat storage tank according to claim 1 or 2, wherein the friction layer 42 formed of a water-permeable fiber lump is formed along a flow path forming surface of the water channel. Terminal structure of.   The water flow path 20 is configured to repeat a portion where the cross-sectional area of the flow path suddenly expands from the distal end portion 10a of the branch pipe toward the opening 28 and a curved portion where the flow path is bent or curved. The terminal structure of the water supply or drainage channel of the temperature stratified heat storage tank according to any one of claims 1 to 3. The water flow path 20 is composed of a plurality of flow path portions 20a that overlap each other, and is formed so as to be folded back from one flow path portion to the next flow path portion.
5. The thermal stratification type heat storage tank according to claim 4, wherein the flow path portions are concentrically folded from the inside to the outside around the first one flow path portion formed in a column shape. Terminal structure of water supply or drainage channel. The head member 14 is
A horizontal outward flange-like wall 48 attached to the tip of the branch pipe 10 extending in the vertical direction;
A cylindrical wall 50 protruding in the same direction as the branch pipe from the outer edge of the outward flange-shaped wall;
A support rod 52 protruding from the inside of the main pipe 8 through the branch pipe 10 into the cylindrical wall 50;
A baffle plate 54 attached to the upper end of the support bar and extending toward the inner surface of the cylindrical wall with a certain gap between the outward flange-like wall 48,
The support bar 52 extends along the axis of the branch pipe so as not to touch the inner surface of the branch pipe,
The distance L ₁ between the outer surface of the support bar 52 and the inner surface of the branch pipe 10 and the distance L ₂ between the outer edge of the baffle plate 54 and the inner surface of the cylindrical wall 50 are constant in the circumferential direction, respectively. The terminal structure of the water supply thru | or drainage flow path of the temperature stratification type heat storage tank of 4. A branch pipe extending from a main pipe piped inside or outside the temperature-stratified heat storage tank is provided so as to be usable in a distributor mode or a water collector mode. At least one branch pipe tip and a tip of the branch pipe A terminal structure of a water supply or drainage channel formed by a head member connected to a portion,
The head member 14 is
A tall large-diameter cylindrical portion 16 having one of the upper and lower end faces as an opening 28 and the other closed;
A low-profile, small-diameter cylindrical portion 18 that closes one of the upper and lower end faces and has the other communicating port 24;
A hollow formed by concentrically inserting the small diameter cylindrical portion 18 into the back of the large diameter cylindrical portion 16 so that the closed end of the large diameter cylindrical portion 16 and the communication port 24 of the small diameter cylindrical portion 18 face each other. Body,
The distal end portion 10a of the branch pipe 10 is inserted through appropriate positions of the large diameter cylindrical portion 16 and the small diameter cylindrical portion 18,
A temperature-stratified heat storage tank characterized in that a water passage 20 is formed from the tip portion to the inside of the small-diameter cylindrical portion and through the gap between the cylindrical walls of the small-diameter cylindrical portion and the large-diameter cylindrical portion to the opening 28. Terminal structure of water supply or drainage channel.   The head member 14 is opened when filling the heat storage tank 2 with water or sucking water from the heat storage tank 2 on the opposite side of the opening 28 and closes when storing heat or releasing heat. The terminal structure of the water supply or drainage flow path of the temperature stratified heat storage tank according to claim 1, wherein a valve mechanism 60 for extraction is provided. A water supply main pipe 8 is connected to one of the upper and lower parts of the tank, and a drain main pipe 8 is connected to the other, and a distributor E _{1 is connected} to the tip of the branch pipe 10 from the water supply side main pipe 8, and the drain side main pipe 8 is connected. at a temperature stratified storage tank comprising a water collecting unit E ₂ is attached respectively to the tip of the branch pipe 10 from,
The distributor E ₁ and the water collector E ₂ have a terminal structure of a water supply or drainage channel according to any one of claims 1 to 8,
Of the openings 28 of the distributors E _{1 to} E ₂ , those that are connected to the lower main pipe 8 face downward toward the bottom of the heat storage tank 2, and those that are connected to the upper main pipe 8 are those of the heat storage tank 2. A temperature-stratified heat storage tank characterized by being oriented upward facing the upper end surface.

Images